Gear generator



Dec. 14, 1943. w. E. SYKES GEAR GENERATOR Original Filed Dec. 28, 1938 8Sheets-Sheet 1 Dec, 14,1943. ,w. E. sYKEs GEAR GENERAT OR a Sheets-Sheet2 Original Filed Dec. 28, 1938 Dec. 14, 1943. w. E. sYKEs 2,336,760

. GEAR GENERATOR Original Filed Dec. 28, 1938 B SheetS-Sheet 3 w. E. SYKES em GENERATOR Original Filed Dec. 28, 1938 a sneetssne'et 5 14, .3- w.E. SYKES 2,336,760,

GEAR emmnmon Original Filed Dec. 28, 1938 a Sheets-Sheet e ul IIIII w vI v v I. u 1

Dec. 14, 1943. w. E. SYKES GEAR GENERATOR Original Filed Dec. 28, 1938 sSheets-She et '7 I l vzleni or wz'ZZ-z'am E Sykes w. E. SYKES v2,336,760

em GENERATOR Original Filgd Dec. 28, 1938 8 Sheets-Sheet 8 Even-E07Patented Dec. 14, 1943 GEAR- GENERATOR William Edwin Sykes, Manor Works,Staines, England; Beatrice Mary Sykes and John T.

Golby executors of sai deceased d William Edwin Sykes,

Original application December 28, 1938, Serial No. 248,090, now PatentNo. 2,306,910, dated December 29, 1942. Divided and this applicationOctober 20, 1942 Great Britain October 8 Claims.

This case is a division of my prior United States application Serial No.248,090, filed December 28. 1938, now Patent No. 2,306,910, datedDecember 29, 1942, which in turn invoked the benefits attending thefiling of applications in Great Britain for the same subject matter onor about October 29, 1938, Serial Nos. 31,328/38 and 3l,329/38, nowPatents No. 508,638 and No. 508,- 639 respectively.

As stated in the specification of my parent United States applicationSerial No. 248,090, the herein-described invention relates toimprovements in machines for cutting gears of the straight or helicaltype. The following description will discuss a preferred embodiment ofthe machine in its entirety, but, as will appear from the followingclaims, the particular subject matter here to be considered relates toan in-feed and related mechanism useful in such machine tools.

In a general view, the invention is particularly directed to machineswhich operate on the molding-generating principle of action-commonlycalled gear shapers. machine of this type which is readily adapted tomodern mass production without sacrifice of accuracy in the cuttingoperations. In attaining this object, provision is made to utilize anovel in-feed mechanism cooperating with a work saddle, whereby the workis advanced to the cutting tool in intermittent steps, and'is withdrawnwhen the machining operation is completed. Such feeding is, moreover,coordinated with the action of the cutter itself.

The various features and principles of the invention and the operatingadvantages to be derived from the use thereof will be apparent from aperusal of the following description, in which reference is made to theaccompanying drawings, wherein:

Fig. l is a side elevation of the gear shaper;

Figs. 2 and 3 are front and rear elevations respectively;

Fig. 4 is a section on the line 4-4 of Fig. 1;

Fig. 5 is an enlarged section on the line 5-5 of Fig. 1, showing the topdrive mechanism;

Figs. 6 and 7 are sections on the lines 6-6 and 7-? respectively of Fig.5;

Fig. 8 is a fragmentary section on the line 8-9 of Fig. 5, showing theclutch operating device;

Fig. 9 is an enlarged section on the line 9-9 of Fig. 2, showing thedriving connections of the cutter head;

Fig. 10 is a section on the line Iii-l9 of Fig. 9; Fig. 11 is a sectionon the line ll-ll of Fig. 9,

, Serial No. 462,767. In

One object is to provide a showing the cam arrangement for obtaining therelief movement of the cutter head;

Fig. 12 is an'enlarged front view of the in feed control mechanism, withthe cover broken away;

Fig. 13 is an enlarged section on the line l3-l3 of Fig. 1, showing thedriving connections of the in-feed mechanism;

Fig. 14 is an enlarged section on the line 14-14 of Fig. 1, showing theWork saddle details;

Fig. 15 is a perspective View of the Work saddle crosshead and thecomplementary in-feed cam block;

Fig. 16 is a section on the line Iii-l6 of Fig. 4, showing details ofthe tailstock structure.

The machine operates on the so-called shaping-generating principle ofaction. wherein a cutter C and a gear blank G (Fig. l) revolve togetheras if in perfect mesh, while the cutter additionally reciprocatesaxially in simulation of a shaper cutting stroke. In the use of thepresent machine, the chief duty of the operator is to remove thefinished gear or gears, and to affix new blanks in the work saddle,since the operating cycle including the in-feed of the blank, stoppingof the machine, and repositioning of the work saddle, may be madeentirely automatic. One operator may therefore attend a number ofmachines, which, as will be observed in Fig. 2, are relatively narrowand straight sided, so that they may be arranged in a compact battery.It will be noted that various adjustable means are conveniently locatedon the front or operating side of the machine, while the timing gearsare all accessible through the rear of the machine housing, as shown inFig. 3.

The machine frame includes a base and a su erimposed pedestal 3|, whichis formed with a timing gear compartment 32 having a rear opening 33covered by a door 34 (Fig. l). The flat top 35 of the pedestal 3|receives the drive unit D of the machine, while the front wall 36 of thecompartment 32 serves as a support for the cutter head unit H. Theremaining major components of the machine, consisting of the work saddleunit S and the in-feed unit F, are disposed on the base 30.

The drive unit pulley 45 secured to its shaft, and it is connected tooperate the pulley 43 by V belts 46. Bevel gears 48, 49 are keyed to theshaft 40, and they mesh with gears I,.52 which are carried by.

countershafts 53, 54- respectively. A third bevel gear 55, rotatablycarried on the shaft 40 and positioned by a spacing sleeve 56, mesheswith a bevel gear 51 keyed to an angularly disposed countershaft 58(Fig. 6). A clutch connection is provided to connect the gear 55totheshaft 48 in a manner presently to be described.

The positively driven countershafts 53jand 54' by the clutch connectionbetween the gear 55 and the drive shaft 58 which permits instantcessation of the generating and in-feed movements without the necessityof stopping the motor 44.

As will be seen in Figs. Sandi the connection includes a clutch element60 which is slidably keyed to the shaft 42!, and which is formed withteeth 59. The gear 55is, formed with complementary clutch teeth El. Anactuator yoke 62lengages a groove 63in the element 68, and it is securedto a rod 64, one end of which is carried in a bearing 65, while theother end. projects through the front ofthe housing 38. A small casing61 (Fig. 8) is secured to this portion of the housing, and it containsvertically aligned bearings 68, 69 for a control shaft I0, to the upperend of which is secured an eccentric II. An eccentric strap 12 engagesthe eccentric] I; and it is secured to the projecting endof the rod 6 1,and the strapadditionally receives a spring M which engages the outerwall ofthe casing $1, and thus constantly thrusts the rod inward. Thelower extremityof the shaft I0. is supplied witha lever 75.. which, whenturned to the right from the position of Fig. 2,.moves the eccentric sothat the rod 5 3 and accompanying clutch element (is are moved inward toconnect the element with the gear '55.

Referring now to the horizontal countershait 53 (Fig. 5), it will beobserved that it projects through a bearing. 16, in the housing 38 andis connected to a companion shaft 53a by a coupling TI. The lattershaft. is mounted inbearings E8 in an adjacent gear box 88, and it.carries a gear BI which meshes with a gear 82 secured to a crankshaft83. The crankshaft is carried in bear,- ings 85, 85 in the gear box,andits projecting extremity is formed with a T-slot B! for receiving astud 88..which serves as an adjustable crank pin. A rollerbearingstructure 89 which is fitted to the crank pin receives th big end 91 ofa connecting. rod 96, and the bearing structure and crank pin are heldin place by a cover plate 92 and a clamping nut 93 on the pin 88. Theconnecting rod 58 will also be observed in Fig. 9. It will be apparentthat by loosening the nut 93 and sliding the pin in the T-slot 3?, theeffective stroke of theconnecting rod maybe varied. As will presentlybe-described, the connecting rod 951 imparts reciprocatory movementtothe cutter C, and thus the stroke adjustment permits the cutter to beadapted to the width of the ear blank or blanks about to be machined.

The cutter unit The lower end of the connecting rod S is bifurcated asindicated by the numeral 95 (Figs. 2 and 9), toreceive the head- 98' of,a stud 5? which serves as a link connection tothe guide or cross-headstructure of the cutter unit (Figs. 9 and The end 95 receives a wristpin in the form of. a bolt 93 having an eccentric 9B keyed to it. Theeccentric is mounted in a bearing ifii in the stud 91. The eccentric isnormally retained in a fixed position by the clamping force applied bynuts I52 on the bolt .33 (Fig. 2). It will be apparent that theeccentric may be clamped in any desired position, thus serving as anadjustable connection between the connecting rod and the cross-head.

The cross-head consists of a guide Hi0 and a spindle I84 which arerigidly secured together by a connection N35. The guide is bored toreceive a multiple ball bearing structure Iiili, the inner racesof'which are rigidly clamped to the stern Id! of; the studfi! bylocknuts I98. The outer. races of the bearing structure areretainedwbetween a, shoulder Hi9 in the guide bore and a thrust platelill'which is secured to the upper endof the guide I80. The cross-head,althoughthus definitely coupled to the connecting rod 90, isadditionally rotatably mounted on the stud 9? through the bearingstructure. The spindle I84 of the cross-head is formed with a threadedhole 184a, which serves to receive a tool post C to which the cutter Cis secured. Instead of the-ball bearing structure I 35, one or morethrust rings may be employed to connect the cross-head andstud S7.

The spindle IM- is supported by a vertical. bearing H2 forming part ofacutter head H3 which: in turn is carried by a bracket Sit secured'tothe frontwall 36' of the pedestal (Figs. 9 and 10). A cylindricalbushing 555 is secured tothe top of the head HS, and its inner bearingwall II5ais concentrically spaced from the guide, It?) to receiverotatably an interposed sleeve: HE. A wormwheel IN. is bored to fit theouter wall H5?) of'the bushing HF, and it is also formedtwith anelongated hub H8. which extends upward for connectionwiththe flange II9.:of the' leeve'l iii.

The;worm Wheel I26 and sleeve iii, which may beconsidered aunitarystructure in effect, are connected. tothe guide Hi9 of the cross-head bykeysI 2i, which are carried by the sleeve I I5 and which engage instraight keyways I22 in the guide Iiifi. As will be seen in Figs. 9 and10, each key IZI is. formed oitwo complementary, wedgeshaped sections I2 lo, I 2 lb, one of which is rigidly secured to the sleeve by screwsIII. The other section ,I2Ib isaxiallymovable by an adjusting screw IIla, to permit takeup for wear.

A casing I23, secured to the upper end of the cutter head H3, and acover I24 which is se cured to the casing, form a protective enclosurefor the worm wheel I29. A Worm casing I25 is secured to the-left handside of the casing I 23 (Fig. 10) and it contains suitable bearingsI24a, I241), fora worm shaft ITS, which projects through an opening I21in the wall 36 and into the timing gear compartment-32. A worm I38,carried by the shaft I26, drives the Worm wheel I20, and:with it theattached sleeve H6;

As; thus far described, it will be apparent that asthe cross-headisreciprocated by the crank mechanism, it also receives a rotarymovement through the drive afforded by worm I39, worm wheel I20, and thekey connection between the guide idil and the sleeve IE6.

Cutter relief mechanism Referring again to the cutter bracket H4, itwill be noted that the lower portion thereof (Figs. 9, 10, and 11) isformed with a chamber lid-a, in which are disposed attached side platesiEI, I38, and a bottom plate 532, which, together with the wall i33 ofthe bracket, form a box bearing for receiving the rectilinear projectionI35 of the cutter head H3. A wedge plate 13% is interposed between oneplate is! and the adjacent wall I3? to provide lateral adjusting meansfor the bearing structure. The lower surface of the cutter head containsa square way I 39 which is angularly disposed and is adapted to receivea cam member I The square ends iii, M2 of the cam member are received inlaterally aligned bearing apertures lSla, I 33a in the side plates Hiand E33.

A tappet I l-3 is secured to the end 5 32 of the cam member Hit, and itis engaged by a cam Hi5 which is secured to a vertical shaft Evie. Thisshaft is carried in a suitable bearing in a box M5 secured to the sideof the bracket I44 and it eX- tends upward for connection with thecountershaft E l by a coupling Ml (Fig. 7).

The timing of the drive mechanisms is such that during eachreciprocatory cycle of the de scribed cross-head (i. e., the downwardand the return movement), the cam 555 performs a complete revolution.During the initial part of the downward or active cutting stroke of thecrosshead, the large cam member M 9 is thrust to the I right (Fig. 11)by springs i is, hit, until the cutter head is slid outwaix to its fullextended position against a stop member I M, which is secured to theplate 532. During this portion of the stroke, the rotating cam hi5presents its dwell portion Mfia to the tappet i is, and is just clear ofthe tappet, and thus does not touch the cam member I49. However, as theend of the cutting stroke is reached, the lobe M579 of the cam engagesthe tappet Hi3 and thrusts the cam member MB to the left against theurge of the springs i l-8, ids. This causes the cutter head to recedeslightly within the box bearing of the bracket lid to a relief positionwhich is retained during the upward stroke of the cross-head.

Timing gear The previously mentioned clutch controlled countershaft 53(Figs. 3 and 6) extends through an aperture in the pedestal top 35 andinto the compartment 3s where it is coupled to an aligned shaft 530:.From this point the gearing is disposed and proportioned to transmit theproper relative speeds to the worm shaft E25, which causes rotation ofthe cross-head, and a work shaft i Ell which drives the work andiii-feed units S and F.

As shown diagrammatically in Figs. 1 and 3, the shaft 58a carries abevel gear 953 which meshes with a gear Ills carried by a horizontalshaft E55. ihe latter shaft carries a second gear 5534: which drives areducing gear cluster E55, the final shaft l5? of which carries a gearI553. From here the drive is split, as two opposed gears its and iii!mesh with the gear Hi5, "lg attached to the worm shaft tit and thelatbeing attached to a shaft 52, which drives a second gear clusterEtta. The final gear its of the second gear cluster meshes with a gear i35: which is secured to the work shaft I50.

the former be- The gear clusters I56, I561; each include a group ofgears which are removable and replaceable by other gears when it isdesired to change the speed ratio between the worm and work shafts 1'26,I and/or between the main drive and both of these shafts. Inasmuch asclusters of this nature are well known in the mechanical arts, adetailed description thereof does not appear necessary, save to mentionthat they are disposed in a position (Fig. 3) where they areconveniently accessible through the rear opening 33 in the timing gearcompartment 32.

Work saddle unit A saddle ill; (Figs. 1, 4, and 14), mounted for slidingmovement on the machine base 38, is provided with gibs IE5, IE'I whichare received in complementary ways its in the base. A cover IlI issecured to the saddle, and it and the saddle are supplied with alignedbushings Ilfla, Illa, which receive a rotatable work spindle Hill. Thespindle is formed with a central radial flange 9 l2 which is retainedbetween thrust surfaces Iltb, llIb of the saddle and cover respectivelyby interposed thrust washers 169, H3.

The spindle E66 is rotated by a worm Il=l which meshes with a worm wheelformation ilE on the periphery of the spindle flange H2. The worm H4 isslidably splined to the previously mentioned work shaft I50, and it iscarried in bearings H6 located in a worm casing 14a which is secured tothe side of the saddle ilt. It will be observed that the bearings areposition the worm against axial movement so that as the saddle is movedthe worm is carried with it along the axially fixed shaft hill.

A table Ill is secured to the upper end of the spindle 589, and itserves as a mounting base for the gear blank or blanks G which may becarried on an arbor Ilt, which is secured in the bore Ideaof thespindle.

Where the relative proportions of the work demand it, a tailstock Ids isutilized to support the upper end of the work arbor Elli. As shown inFigs. 1, 2, 4, and 16, the tailstock includes a base i9I which issecured to the cover IlI of the saddle and which carries spaced verticalguide pins I92 having rack formations IQZa thereon. A yoke I93 is formedwith vertical bearings IQSa, which slidably receive the pins I92, andhorizontal bearings i931) for receiving a shaft I94. Gears I95 aresecured to the shaft I94, and they are housed in pockets idea in theyoke B93 and are disposed to mesh with the rack formations IflZa on thepins and thus assure proper parallel movement of the yoke when it isadjusted to various heights. The bearings I33a are split, as indicatedby the numeral 593, and they are formed with drilled lugs ldl forreceiving a bolt ltla which is utilized to lock the yoke to the pinsI92.

The yoke 1&3 is formed with a central projection I98 which contains avertical gib portion I59 for receiving a dead center 2%, whose body isformed with a complementary gib portion Zli. A clamping slide strip 252is disposed to engage a second gib portion 2&3 on the center and it istapped to receive a transverse screw which projects through to the frontof the yoke I93 where it receives a handle 2335a. A plate which issecured to the top of the center 2%, is carried by a vertical screw 2%disposed in a suitable tapped hole'in the projection we. The screw 2%may be operated to raise or lower the plate 2E5'and accompanyingcenterZilil to proper adjustment, whereupon the center fiililuisrigidlyclamped byturning the'handle 224a wliich'draws up the clamping strip232.

In-feed unit A red (Fig. 13) which is secured to the saddle Hi3 projectsinto the adjacent in-feed unit F, and it is operated by the mechanism ofthe unit to move the saddle step by step towards the cutter, until thefull depth of the gear tooth is attained, whereupon the rod andaccompanying saddle are automatically withdrawn. As shown in Fig. 14,the rod is threaded to enter a tapped hole 2 in the saddle, and islocked thereto by a suitable lock nut.

The unit F includes a housing 229 having a horizontal slide portion 22|which receives a slide block 222 (Figs. 13 and 15). The rod 210 r. .in

projects through a hole 228 in the block and,

it is secured against axial displacement in the bearing structure bylock nuts 225. The block is slotted as indicated by the numeral 225, andscrews 221 are transversely positioned through the slotted portion toprovide a clamp for securing the rod against rotation in the blockbearings.

The rod 2! projects through the block 222 to the front of the machine,where it may be manuaily operated when it is desired to adjust the position of the saddle.

A transversely positioned control block 23% is disposed immediatelybeneath the forward end of the clock 222 and it is guided in transverserails 235 formed in the housing 220 of the in-feed unit. The uppersurface of the control block 2% contains an angular cam groove 232 (Fig.15), while the adjoining surface of the block 222 is formed with acomplementary cam portion 233. The control block contains sockets 234for receiving compression springs 235 which bear against the adjacentwall 236 of the housing and thus urge the block to the left (Fig. 12)The control block is automatically locked against such spring-impelledmovement by a mechanism consisting of rollers 231, 231a, which aredisposed between the lower surface 239a of the control block and theangular surface 238?) of a hardened insert 233, which is aflixed to thehousing 22%. The rollers are constantly urged into looking position by aspring-pressed plunger 239 which is likewise disposed beneath thecontrol block. A release finger 2M! is located to the left of therollers, and it is formed with a projection which, as will presently bedescribed, is enhy other mechanism whereby the rollers are moved to theright to release the control Llock for the spring-impelled movement.

t will be apparent that when the control block 23% is moved to theright, the saddle slide block and accompanying saddle I ii! are movedtoward the cutter C. At the same time the springs are compressed inpreparation for release of the block 2313, and when such release occurs,the control block is moved to the left and the saddle is accordinglymoved away from the cutter.

The advance movement of the control bloclr that s, movement to the rightthereof, which results in advance of the saddle toward the cutter, isoperated by a control mechanism driven by the work shaft 559. This shaftextends into the housing 223 where it is carried in suitable bearings.An adjoining cam shaft 246, which is mounted in suitablebearings in thehousing 229..

secured to the shafts. The cam shaft 2% carries a cam 246a whichoperates a ratchet mechanism for driving a control mechanism 256 foradvancing the control block.

The control mechanism includes a fixed shaft 2'5! which is secured in aboss structure 252 in the housing 22% and which rotatably carries a pawlarm 253. A lobe 25E on the extremity of the pawl arm is retained incontact with the cam 246a by a compression spring 255. A ratchet wheel25% which is secured to a bearing sleeve 25'! on the fixed shaft 25! isengaged by a spring-pressed pawl 284 carried by a stud 253 on theratchet arm 253. A spring-pressed ratchet 259, conveniently carried onan adjacent shaft 266, which will be described later, engages theratchet wheel against retrogressive movement. As thus far described, itwill be seen that as the cam shaft 2% is rotated, the pawl arm 253 isoscillated to cause intermittent rotation of the ratchet wheel 253 in aclockwise direction.

The bearing sleeve 25'! also carries a control disc 262 which containsspaced radial slots 263 and an angular slot 264 for receiving studs 265,265 on which cam rollers 265a, 2660. are rotatably mounted. A segmentalcam insert 237 is secured to the disc, and it projects therefrom in thesame plane as the rollers. The rollers, in counterclockwise order, arepositioned at progressively greater radial distances from the axis ofthe disc 262, and, as the disc is rotated, they successively engage theleft face 2360 of the control block 230, and thereby move the block tothe right. In Fig. 12, the first roller 256a has just engaged the blockto start the feed cycle of the saddle, and it is followed by the secondand third rollers, and finally the cam insert 28?. The cam insert has acam face 251a and a radial dwell face 25%, the former face engaging andmoving the block 230 a slight distance to give a final and finishingmovement to the saddle, and the latter face retaining the block in suchfinal position for a considerable period.

The cam insert 28? is a little wider than rollers 265a, and the extrawidth makes contact with and thrusts the release finger am to the right.and, as it leaves the contact face 23%0 of the control block, ittemporarily holds the finger 240 in such depressed position to permitthe block to be restored to its first position by the springs 235. Asthe block returns, it strikes a spring-pressed plunger Zlil (dottedlines, Fig. 12) which is carried for sliding movement in a bearing 2'inthe housing. As the plunger is moved to the left, a pin 210a, carriedthereby, engages and throws a switch arm 2'52 to open the circuit of themotor 54, thus stopping all movement of the machine elements.

To restart the machine, it is necessary to turn the control disc 262manually a slight distance to permit release of the plunger 218 and theclosing of the switch arm 2'52, This starting mechanism includes thepreviously mentioned shaft 26% which is mounted in suitable hearings inthe housing and which protrudes from the housing and is formed with asquare end 2690. for rcceiving a suitable crank. The shaft 2% carries apinion 214 which meshes with a gear Ell? carried by the control sleeve25?.

simultaneously a plurality of gears of relatively narrow facedimensions, or in the alternative to machine a single gear having a wideface. One method of setting up the machine to provide a group cuttingoperation is shown in Fig. 1. As here illustrated, the cutter C consistsof similar cutter elements 289, 28!, carried by the tool post C which inturn is carried by the spindle lot of the cutter unit cross-head.

The cutter elements are in the form of pinions having cutting teeth 283which are axially aligned, and whose cutting edges 284 lie in the samecommon reference surface. A multi-edged cutter is thus provided, whereinthe axial spacing of the elements is equal to the face width of theblanks G which are carried in parallelism on the adjoining work spindle.For proper operation of the machine, the stroke of the crosshead isadjusted so that it is slightly greater than the axial pitch of thecutter elements, with the result that an overlap of the strokes ofadjacent elements is obtained. Inasmuch as the cutting elements are ofidentical formation, the gear blanks are formed with teeth which areuniform in character and which are devoid of tool marks or anydisfigurement.

Where it is desired to dispense with the short stroke method aboveoutlined, the cutter may be of the usual single form. In this instancethe usual practice may be followed in adjusting the stroke of the cutterto be slightly greater than the face width of the gear blank. t will beunderstood that the cutters may be of either the straig t tooth orhelical types. In the use of elical cutters, the cross-head guide Wemust be modified to contain helical keyways to obtain an additionalhelical twist during each stroke, as is well known in the art.

I claim:

In a gear shaper of the character described, a work saddle mounted forlineal movement, an in-feed mechanism for the work saddle comprising ablock carried by the saddle, a block mounted for transverse slidingmovement relative to said first block, a complementary cam connectionbetween the blocks whereby movement of the second block causestransverse movement of the first block and accompanying saddle,intermittently operated means for moving the second block in onedirection, springs for resisting said movement, means for locking thesecond block against spring-impelled movement, and automatic releasemeans for said locking means for releasing the block for spring-impelledmovement in a direction of movement opposite to said intermittentlyoperated movement.

2. In a gear shaper of the character described, a work saddle mountedfor lineal movement, an in-feed mechanism for tr e work saddlecomprising a block carried by the saddle, a block mounted for transversesliding movement relative to said first block, a complementary camconnection between the blocks, a driven rotatable spindle, a controldisc secured to the spindle and having a plurality of radially spacedactuating members secured thereto, said members being substantiallyspirally disposed relative to each other and to the axis of the spindle,said actuating members being disposed to engage the second block to movethe block in progressive steps in one direction, and mechanism forautomatically returning said second block to its sta g position afterthe disc has completed its cycle.

3. In a gear shaper of the character described, an iii-feed mechanismfor a work saddle com- 5 prising an intermittently rotated spindle, acontrol disc secured to the spindle and having a plurality of radiallyspaced actuating members secured thereto, said members beingsubstantially spirally disposed relative to each other and to the axisof the spindle, a block mounted for transverse movement relative to theaxis of the spindle and being disposed to be engaged progressively andmoved in one direction by the members, spring means for resisting suchmovement, means locking said block against spring-impelled movement,release means for said locking means operable by the outermost of saidactuating members, and a connection between the block and said saddle.

l. In a machine of the class described, a work saddle, and in-fcedmechanism for progressively moving the work against a cutting toolembodied in the machine, said in-ieed mechanism comprising a slide blockconnected to the saddle, an angularly disposed control block engagingsaid slide block to thrust the slide block and saddle toward said toolas said control block is moved laterally with respect thereto, springmeans for urging the control block in one direction, said control block,when moved by said spring means, withdrawing the sllde block and saddlemom said cutting tool, means 101' intermittently moving tne controlblock against the urge or the spring means, means Ior locking thecontrol block in the position into which it is moved, and means actuatedby the intermittently moving means Ior releasing the locking meansW116i]. said control block has been moved against the spring means to apredetermined position.

5. ln-r'eed mechanism for the work saddle or a machine tool comprising apower shalt and an actuating disc, means for intermittently supplyingpower from the power shart to the disc to cause progressive rotarymovement thereof, a linearly movable control block mounted for slidingmovement adjacent the actuating disc, spirally disposed members on thedisc adapted to engage the control block as the disc rotates and therebythrust the block in one lineal direction, spring opposing movement ofthe control block in said direction and urging its movement in anopposite direction, a lOCKll'lg means engaging the control block andholding the same in the positron determined by the rotation of the disc,a release finger contacting the locking means, said linger being engagedby the last of said spirally disposed members only to cause the lingerto release tl'le locking means at a predetermined position in therotation of the disc, and a slide movaIoly connected to the controlblock to cause the saddle to move in proportion to the movements of thecontrol block.

6. In-feed mechanism for the work saddle of a machine tool wherein thereis a power source, comprising a slide block connected to the saddle andadapted by its movement to move the saddle toward or away from the tool,an angularly disposed control block movably connected to the slideblock, a rotary actuator disc provided with spirally disposed membersadapted to engage the control block successively to move it in onedirection, spring means for urging the control block in the oppositedirection, a lock for holding the control block against the springs,means engageable by one of the spirally disposed members to deconditionthe lock to permit return of the control block, means actuated by thepower source for rotating the actuator disc, and a trip actuated by -'7.In-feed mechanismior the-work saddle of a machine-tool comprising a;saddle. ,mounted'for lineal movement in opposite directions, aslideblock connected to the saddle, said blocksbeing formed with a diagonallydisposed camelement a control block mounted for sliding movement in twooppOsite directions and angularly disposed with respect to the .slideblock, a,comp lement ary diagonally disposed camonthe control "blockengaging the cam on the slide block and, consti s id bl c s fo simu tanous. movement a guideway in whichthecontrol block may move,

advancing means engaging one end ofthecontrol block to advance itprogressively in one direction as said n n means s cac u te r pringmeanengaging the opposite endflof the'controlblock and constantly urgingitin the opposite direction, a roller r a s i t mosed .b tween the cont;;the control block when; moved by said spring m an f d conn ctin t e:pw r source.

8. ln feed mechanism fora machine tool com- ;prisingarslide' blockmounted for movement in opposite lineal directions, a control blockmounted for lineal movement in atransverse direction,

complementary cam members; on the blocks diagonally-disposed withrespect to the lines of movement thereof for interconnecting the blocksand causing the sameto move simultaneously,

cspringmeans for urging the control block in one direction and therebythe slide block, a rotary actuator for progressively movin the controlblockflagainst the urge of the spring means, said actuator, engagingthecontrol block through less than acomplete circumference to permitreturn of the block by the spring during one phase of rotationthereof,a. lock engaging the slide block to hold it in theuposition to which itis moved by the-actuator, a release member for disengaging the lock,,andmeanson the actuator engaging the release member during said phase ofrotation to decondition the lock and thereby permit return ofthe controlblock.

WILLIAM EDWIN SYKES.

